Cutting device

ABSTRACT

A cutting assembly comprising a plurality of interposed rollertype cutters that are driven by a prime mover through a torque transmitting device. Also, a feed material conveying device is provided which includes converging live-roll conveyors for simultaneously transporting, crushing and compacting the material being handled prior to insertion into said cutters.

0 United States Patent [151 3,643,591

Bragg Feb. 22, 1972 [54] CUTTING DEVICE 2,150,984 3/1939 Near et al. ..l00/95 X 72] Inventor: Charles Gail Bragg, 1238 York Avenue, ggggifi 5 132; g ff "241/ l 86 Corpus Christi Tex. a a est) in 3,489,354 l/l970 Harper et al. [00/176 UX [22] Filed: Mar. 30, 1970 3,504,621 4/1970 Qualheim ..l00/l 76 X [21] Primary ExaminerBilly J. Wilhite Attorney-John Paul Robinson, Jr. [52] US. Cl ..l00/95, 83/345, 83/591,

100/ l 76 [57] ABSTRACT A cutting assembly comprising a plurality of interposed rollertype cutters that are driven by a prime mover through a torque transmitting device. Also, a feed material conveying device is 56] References Cited provided which includes converging live-roll conveyors for simultaneously transporting, crushing and compacting the UNITED STATES PATENTS material being handled prior to insertion into said cutters.

1,656,063 l/ 1928 Harrison ..100/95 UX 11 Claims, 7 Drawing Figures BALE-F3 PATENTEDFEB22 I972 3.643 .591

SHEET 1 OF 2 INVENTO CHARLIE 11.. BRAGG ATTORNEY:

PAIENTEDFEH22 I972 3.643.591

sumaurz INVENTOR: CHARLES GAIL BRAGG CUTTING DEVICE The invention relates to a cutting device and more particularly to a device for conveying and simultaneously compressing material being handled prior to insertion between a plurality of interposed roller-type cutters.

In the past, continuous and expensive efforts have been expended to develop a satisfactory and reliable apparatus for reducing stock material to a convenient size which is efficient and quiet in operation, creates only a negligible amount of dust and produces a desired size of stock material for baling. Some of these previous mechanisms included hammer-mills or hoggers and other type of apparatus for pulverizing the stock material being handled. Several persistent defects and/or problems associated with hammer-mills or hoggers have been discovered. For example, these hammer-mills or hoggers require a great amount of power, the noise factor is too great, stock material is reduced to a relative small size whereby baling is difficult, also an unusually large amount of dust is disseminated throughout the ambient atmosphere, thereby creating an extremely dangerous fire hazard. Thus, hammer-mills frequently cause fires and/or explosions, as sparks are created in such a dust ladened atmosphere when the mills fast moving hammers strike a piece of stray metal. Thus, a satisfactory solution has not previously been discovered.

Accordingly, an object of the present invention is the provision of a new and improved cutting apparatus which is reliable in operation, simple to fabricate and is constructed and arranged to minimize overloading of apparatus caused by jamups of material being handled in advance of the roll-type cutters, which results in increased production and operating efficiency, as well as preventing damage to said apparatus.

Another object is to provide a cutting apparatus which is inexpensive to operate and is economical to construct and main tain.

A further object of the present invention is to provide a cutting apparatus which can be kept running with a minimum of downtime due to malfunction of said apparatus, thus maintenance personnel can work on other jobs, thereby increasing savings even more.

A still further object of the present invention is to provide a cutting apparatus which because of its compactness and simplicity of design has a field of its own, as this type of cutting apparatus can be readily installed near a source of paper stock orothcr desired material at reasonable expense.

An additional object of the present invention is to provide a cutting apparatus which can ensure a substantially perfect shearing cut upon the material being handled, thereby producing a desired product.

A still further major object of the present invention is the provision of positively moving the material handled through interposed roller-type cutters at a greater linear speed than the linear speed of material which is being fed to said roller-type cutters, thus substantially eliminating jam-ups of material in advance of a said cutter.

An additional object of the present invention is to provide a cutting apparatus that is so constructed and arranged to stall when the cutters contact large pieces of wood or steel, thereby preventing damage to said cutting apparatus. Also, these large pieces of wood or steel are objectionable and it is advantageous to keep them out of the end product.

A still further object of the present invention is to provide a cutting device that is constructed and arranged to greatly reduce the power requirements of said cutting device. For example, the average hammer-mill will require horsepower or more for each ton per hour of capacity, while the present cutting device handles up to three tons per hour on 7.5 horsepower or 2.5 horsepower for each ton per hour capacity.

Another further object of the present invention is to provide a material handling system which, because of its compactness and simplicity, can be installed on an existing flat floor and there is no need for specially constructed trenches or floor pus.

Other objects and purposes of this invention will be apparent to persons acquainted with cutting apparatus of this general type upon reading the following specification in conjunction with the accompanying drawing.

ln the drawing:

FIG. 1 is a schematic illustrating a material-handling system in which the present inventive concept can be employed;

FIG. ll is a fragmentary oblique view illustrating the drive means of the present cutting device;

FIG. lll is an oblique view of the present inventive concept;

FIGS. IV, V, VI each show an enlarged fragmentary sectional view showing each of the final roll elements having a plurality of lugs radially disposed in different positions as said roll elements rotate through an angle of 45.

FIG. Vll is a fragmentary view in elevation of the present cutting device.

Certain terminology will be used in the following description for convenience in reference only and will not be limiting. The words upwardly, downwardly, rightwardly," and leftwardly" will designate directions in the drawing in which reference is made. The words inwardly" and outwardly will refer to directions toward and away from, respectively, the geometric center of the cutting apparatus and designated parts thereof. Said terminology will include the words above I specifically mentioned, derivative thereof and words of similar import. Further, it will be understood that the following description of the cutting apparatus and operation of certain portions thereof, has been selected for illustrative purposes only as a convenient and appropriate means for acquainting those skilled in the art with the present invention.

It is to be noted all arrows on the drawing indicate the direction of motion and/or travel of the individual portions or elements of the present inventive concept.

For the purpose of disclosure of the cutting device embodying the present invention, reference is now made in greater detail to the drawing wherein like numerals indicate similar parts or portions throughout the several views. FIG. I illustrates a material handling system which includes the present cutting assembly or device 10 as an integral portion or unit thereof. A feed stock inlet or input conveyor 12, of conventional design, receives material 14 from a usual source of supply. The feed stock material 14 usually consists of setup corrugated boxes, flat corrugated sheets or other materials which the user may wish to crush and cut for further processing. The cutting assembly 10 includes superposed upper and lower live-roll or driven conveyors l6 and 18, respectively, which converge toward the roller-type cutters 20, 22; thereby effecting a positive crushing and compressing of the feed stock material being directed into the cutters 20, 22. The upper discharge surface 24 of conveyor 12 is positioned slightly above the upper surface of lower inlet conveyor 18 to achieve a positive delivery and/or transfer of feed stock material 14 from input conveyor 12. Generally, when a liveroll conveyor is utilized to feed roller-type cutters 20, 22, the axis of the individual roll 106 contiguous conveyor 12 is spaced slightly below discharge surface 24 and in this position substantially prevents jam-ups and effects a smooth transfer of feed stock material. And finally, as the feed stock material 14 is discharged from the cutters 20, 22, a conveyor 26 transports the severed material to a conventional baler 28 which subsequently bales the uniformly cut material for shipment. lt is to be noted, that a remarkably uniform, high-density bale is produced by using the compressed and cut material which is emitted from roller-type cutters 20, 22; in fact a bale having 25 percent to 35 percent greater density is not uncommon.

Reference is now made to FIGS. ll and lll which are relied upon to disclose the new and unobvious roller-type cutter assembly 10 comprising a torque transfer or drive means 30 which is utilized to furnish torque simultaneously to a pair of superposed live-roll conveyors l6, l8 and a plurality of interposed roller-type cutters 20, 22. The torque transfer means 30 includes a prime mover 36, for example, a high-speed electric motor is mounted by suitable means on structural frame 38. If desired, a conventional overload switch can be provided for motor 36. In the present inventive concept, a high-speed electric motor 36 is drivingly connected to a belt-type drive assembly or means 40, wherein a pulley 42 is secured to the rotatable output shaft 44 of electric motor 36 for simultaneous rotation therewith at substantially the same speed. The pulley 42 frictionally drives a conventional V-belt 46 which drivingly engages pulley 48 that is attached to rotatable shaft 50 which is mounted for rotation by well known bearing means, such as a pillow block disposed on frame 38. There is a first speed reduction incorporated in the belt drive assembly 40; this speed reduction can be accomplished by establishing a differential in the pitch diameters of pulleys 42 and 48. If desired, however, pulley 42 can be a conventional variable speed reduction pulley. A chain drive assembly or means 54 drivingly interconnects the belt drive assembly and the lower rotatable shaft or arbor 56 which has one set of longitudinally spaced roller-type cutters fixedly secured thereto for simultaneous rotation therewith. The chain drive assembly 54 includes a sprocket 58 which is attached to rotatable shaft 50 for rotation therewith; and a chain 60 drivingly interconnects sprocket 58 and another sprocket 62 that is connected to shaft or arbor 56 which is rotatably supported on frame 38 by a conventional bearing arrangement. Another speed reduction is incorporated in the chain drive assembly 54; and this speed reduction can be accomplished by varying the pitch diameter of sprockets 58,62, and/or by varying the number of teeth thereon.- The rotatable arbors or shafts 56, 64 have respective roller-type cutters 20, 22 fixedly secured thereto, for simultaneous rotation therewith at substantially the same angular velocity. One end portion of shaft 56 carries a spur gear 66 having gear teeth which mesh with gear teeth on spur gear 68 that is fixedly secured to one end portion of shaft 64 and the meshing engagement of the teeth effects rotation of the lower roll-type cutters 20 in a clockwise direction and the upper cutters 22 rotate in the opposite or counterclockwise direction whenever torque is applied to lower spur gear 66.

It should be apparent from the above description, that by employing the combination of a belt drive and chain drive to supply torque from a high-speed electric motor 36 to a pair of superposed roller-type cutter shafts 56, 64 effectively provides a drive means-which combines the advantages of both the belt and chain drives. The advantages claimed for the belt drive are: (a) The initial high speed of a high-speed electric'motor, for example 1,750 r.p.m. (revolutions per minute) or 3,500 r.p.m. almost requires the use of a belt drive that is elastic and can be run' at speeds of up to5,000 feet per minute. Thus, for substantially any desired belt speed, the greater the pitch diameter of the belt pulley or sheave the greater is the power transmitted thereby; (b) A belt drive has flexibility and good shock-absorbing characteristics; (6) A belt drive will adsorb heavy startup torque and sudden or unusual peak loads; (d) Sustained efficiency of approximately 98 percent and under ordinary or normal operating conditions there is practically no slip which causes a relative low temperature rise; and (e) The belt drive requires no lubrication and is a power transmission medium of remarkable operating life.

Likewise, the advantages claimed for the chain drive are: (a) Long life and silent operation; (b) There is a complete absence of slip between the chain and sprocket; (c) The chain drive has a sustained efficiency of about 98 percent; (d) There is no deterioration due to the metal construction and this also accounts for the absence of substantially any effect as a result of atmospheric changes and varying temperatures; and (e) The chain drive is easily detachable and may be replaced without dismantling the cutter thereby resulting in low maintenance cost.

Thus, the roller-type cutters 20,22, as previously noted, are driven indirectly by the electric motor 36 through a belt drive 40 which is drivingly interconnected to chain drive 54 that in turn furnishes power to lower spur gear 66, to effect the rotation of lower roller-type cutters 20 in a clockwise direction and spur gear 66 drives spur gear 68 which effects rotation of roller-type cutters 22 in a counterclockwise direction.

Each roller-type cutter 20, 22 can be fabricated from cast iron, carbon steel, stainless steel, bronze or any other suitable material; and each cutter 20, 22 has an outer diameter which is usually greater that its length. The cutters 20, 22 can be fixedly secured to its respective arbor or shaft 56, 64 by any desired conventional means, such as set screws or keys seated in complementary keyways. The roller-cutters 20 are longitudinally spaced along shaft 56 in such a manner that they effect an interposed relationship with longitudinally spaced rollertype cutters 22 that are fixedly secured by appropriate means to shaft 64. Each roller-type cutter 20 has a cutting edge 78 positioned adjacent each end portion thereof which cooperates with a similar cutting edge 80 on cooperating roller-type cutters 22 to achieve a substantially perfect shear ing cut on each piece of material handled. Moreover, each cutter 20, 22 has a longitudinally extending projection or protuberance 82 on the outer surface thereof, which is substantially coextensive therewith. The protuberance 82 as shown in FIGS. 1, 11, Ill, and V1] is a bar or lug which usually has a rectangular cross-sectional configuration; other configurations, however, can be successfully utilized. These lugs 82 can be positioned substantially parallel to the horizontal axis of shafts 56, 64 or the lugs can be disposed in a spiral and/or helix along the outer surface of each roller-cutter 20, 22 and about the center axis of its respective shaft 56, 64. Therefore, as the feed-stock material is conveyed by live-roll conveyors 16, 18 toward cutters 20, 22, the material is caught, frictionally restrained from retrograde movement and sometimes pierced by lugs 82. Thus undesirably movement of feed-stock material, such as a rolling and/or lateral movement is substantially inhibited. Lugs 82 tend to push or positively force the feed-stock material into and through the roller-type cutters 20, 22, thereby substantially eliminating jam-ups of material in advance of said cutters; and these lugs 82* can be disposed in substantially any angular relationship on the outer surface of roller-type cutters 20, 22.

The upper and lower live-roll conveyors 16, 18, as shown in FIGS. 1, Ill and VII are so constructed and arranged to converge from inlet 86 toward roller-type cutter 20, 22. In the embodiment illustrated, the inclination with respect to a horizontal plane is substantially the same in both the upper and lower live-roll conveyors 16, 18; and each roll element 88, 90, 92, 94 of the upper conveyor 16 is fixedly secured to a complementary rotatable shaft 96, 98, and 102 respectively; and each shaft is rotatably mounted in suitable pillow blocks (not shown) which are carried on frame 38. Likewise, each roll element 106, 108, and 112 of the lower conveyor 18 is fixedly attached to a complementary rotatable shaft 114, 116, 118 and 120, respectively; and each shaft is rotatably mounted in suitable pillow blocks (not shown) which are carried by frame 38. It should be noted, that all of the above noted pillow blocks are mounted outside sidewalls 124 and 126 to prevent grease or oil from getting into the material which is being handled and to prevent said material from clogging the bearings in said pillow blocks. As shown in FIG. [11, roll elements 88, 90, 92, 94, 106, 108, 110 and 112 extend substantially from sidewall 124 to sidewall 126; and with each of said roll elements having at least one protuberance or lug 128 coextensive therewith and substantially parallel to the center axis of shaft members 96, 98, 100, 102, 114, 116, 118 and 120. Thus, as the roll elements are rotated by respective chain and sprocket drive assembly or means 130 and 132, as illustrated in FIG. [11, these lugs 128 grab and forcibly convey the material forwardly from inlet 86 toward the roller-type cutters 20, 22. The roll elements 88 thru 94 of upper conveyor 16 are generally vertically aligned or superposed with respect to cooperating roll elements 106 thru 112; this vertical alignment feature, however, is neither essential or required in the present device; inasmuch as, the roll elements 88 thru 94 of the upper conveyor 16 can be offset with respect to the roll elements106 thru 112 of the lower conveyor 18.

Spur gears 66, 68 which transmit torque to respective rollertype cutters 20, 22, simultaneously transmits torque to chain and sprocket drive means 130 and 132. Sprocket members 134, 136, 138, 140, 142, 144, 146 and 148 are integral portions of respective chain drive means 130 and 132 which drive live-roll conveyors 16, 18. These sprocket members 134 thru 148 drive individual roll elements 88 thru 94 and 106 thru 112 at different speeds so that the linear speed of the outer periphery of each roll varies or is different from the roll element adjacent thereto. For example, a large corrugated paper box can be grasped by lugs 128 positioned on rollers 88, 106 which has a peripheral speed of 107 feet per minute. The box will be partially crushed and moved forwardly toward and between rolls 90 and 108 which have a peripheral speed of about 1 13 feet per minute. During this movement the box is crushed to a still smaller vertical dimension and simultaneously move forwardly at a faster rate of speed. Such action is substantially identical on successive pairs of rollers 92 and 110 and subsequently on rollers 94 and 112. The progressively increasing speeds of the successive pairs of converging rollers and the simultaneous crushing action ensure that the crushed box will be suitably flattened and elongated rather than wadded-up, when it reaches the final step which is cutting or shearing by roller-type cutters 20 and 22. The different speeds of. the individual rolls is accomplished by sprocket members 134 thru 140 and sprocket members 142 thru 148 having a different number of teeth and/or different pitch diameters. The construction and characteristics of the individual sprocket members are shown in the following Table 1.

The periphery of roller-type cutters 20, 22 has a speed of 130 feet per minute; however, this rate of speed can be readily varied as desired. The outer periphery of each cutter 20, 22 has a greater speed than the outer periphery of roll elements 88 thru 94 and 106 thru 112 for the purpose of preventing the jamming of material adjacent said cutters 20, 22. The chain and sprocket drive means 130 and 132 are synchronized to drive the rolls 88-92 and 106-110 at progressively greater speeds from inlet 86 toward roller-type cutters 20, 22 and the lugs 128 on rolls 88-92 and 106-110 are arranged to angularly coincide with corresponding lugs on adjacent rolls (See F IGS. l& V11).

As illustrated in F105. 1V, V and V1, each of the final roll elements 94, 112 has a plurality of lugs 128 radially positioned thereon. in the embodiment shown, the lugs 128 on roll 94 are angularly offset approximately 45 with respect to the lugs 128 on roll 112; so that the distance X" between rolls 94, 112 is generally constant or uniform at all times (preferably 3 inches). It has been determined that when the dimension X" lies in a range between 1% to 4 inches, there is substantially no jam-ups of material in front of roller-type cutters 20, 22.

The operation of the invention will be described with particular reference to its application in the material handling system shown in P16. 1, which includes an input conveyor 12 that transports feed stock material 14 to converging live-roll conveyors 16, 18. Live-roll conveyors 16, 18 simultaneously compress, crush and transport the material 14 at progressively faster linear speeds toward roller-type cutters 20, 22. Any material 14 which may fall between roll elements 106 thru 112 of lower live-roll conveyor 18 is caught by conveyor 26 which extends beneath conveyor 18 for such purpose. As the cut material emerges from roller-type cutters 20, 22, conveyor 26 carries said material to the baler 28 wherein a high-density bale is formed. Since conveyor 26 is of the belt type, a plurality of spaced apart stud elements 27 are attached to or extend through the surface of belt 29. These studs project about onequarter inch above surface 29 and in this position ensure the positive conveyance of the cut material from roll-type cutters 20, 22 to baler 28.

As shown in FIGS. 11 and 111, the roller-type cutters 20, 22 are alternately spaced along drive shafts 56, 64; and each cutter 20, 22 has an adjustable chisel-nose stripper blade disposed in opposed relationship thereto. Each stripper blade 150 is independently adjustable with respect to the other stripper blades; and each blade 150 is carried by structural frame 38. Likewise, each stripper blade 150 is independently adjustable relative to rotatable shaft 56 or 64. thereby preventing the material which is being cut from wrapping about either shaft 56, 64 as it emerges from the interposed rollertype cutters 20, 22.

While the invention has been shown, illustrated, described and disclosed in terms of embodiments or modifications which it has assumed in practice, the scope of the invention should not be deemed to be limited by the precise embodiment or modification therein shown, illustrated, described or disclosed; such other embodiments or modifications intended to be reserved especially as they fall within the scope of the claims here appended.

What is claimed is:

1. A roller-type cutter assembly for transporting, crushing, compacting, and cutting material in combination comprising:

A structural means for supporting said assembly;

a plurality of interposed roller-type cutting means rotatably mounted on the structural means, with each of said rollertype cutting means having spaced apart cutting edges disposed adjacent opposite end portions of said rollertype cutting means and each cutting edge so constructed and arranged to cooperate with a complementary cutting edge on an adjacent interposed roller-type cutting means to effectively cut material that is forced therebetween;

each roller-type cutting means having an outer cylinderlike surface with protuberance means disposed thereon for positively forcing the material into and through the cutting edges;

means for rotating the roller-type cutting means at a predetermined angular velocity; V

a live-roll conveyor assembly including aligned roll members with each roll having an outer cylinderlike surface for transporting material being handled from a source of supply toward the roller-type cutting means, said live-roll conveyor assembly having an inlet positioned adjacent said source of supply and an outlet disposed adjacent said roller-type cutting means;

means for rotatably mounting said roll members on the structural means; and

means for moving the cylinderlike outer surface of each roll member at a peripheral speed which is slower than the peripheral speed of the roller-type cutting means.

2. The roller-type cutter assembly recited in claim 1, wherein each protuberance means is substantially coextensive with its respective roller-type cutting means.

3. The roller-type cutter assembly recited in claim 2, wherein each protuberance means is a metal bar having a rectilinear configuration in cross section.

4. The roller-type cutter assembly recited in claim 2, wherein each protuberance means has a rectilinear configuration in cross section.

5. The roller-cutting assembly recited in claim 1, wherein the rotatable cutting means includes:

A first series of roller-type cutters fixedly secured to a rotatable shaft, said cutters being spaced along the longitudinal length of said shaft, thereby forming an annular recess between each pair of adjacent roller-type cutters;

a second series of roller-type cutters fixedly secured to another rotatable shaft, with said cutters spaced along the longitudinal length of the another shaft and thus forming an annular recess between each pair of adjacent rollertype cutters, with each roller-type cutter of the second series positioned opposite and a portion thereof extending into an opposite annular recess formed between adjacent roller-type cutters of said first series.

6v The roller-type cutter assembly recited in claim I, wherein the live-roll conveyor assembly includes a first liveroll conveyor disposed in opposed relationship with respect to a second live-roll conveyor, said first and second conveyors so constructed and arranged in a converging relationship from the inlet toward the outlet for simultaneously transporting, crushing, and compacting the material being handled as it moves from the source of supply toward the roller-type cutting means.

7. The roller-type cutter assembly recited in claim 6, wherein the converging inclination of the first and second liveroll conveyors with respect to a horizontal plane is substantially the same.

8. The roller-type cutter assembly recited in claim 7, wherein each protuberance means has an angular corner formed by a pair of intersecting planes, said corner so constructed and arranged for positively forcing the material handled into and through the cutting edges.

9. The roller-type cutter assembly recited in claim 1, wherein the means for rotating the roller-type cutting means at a predetermined velocity includes torque transmitting means drivingly connected to the cutting means for effecting rotation thereof, said torque transmitting means including a belt drive assembly drivingly interconnecting a prime mover with a chain drive assembly that is drivingly connected at one end to a portion of said belt drive assembly and at another end to a gear drive means that is drivingly connected to the cutting means for rotating said cutting means at a predetermined angular velocity.

10. The roller-type cutter assembly recited in claim 1, wherein the means for rotating the cylinderlike outer surface of each roll member includes means for moving the outer surface of adjacent roll members at progressively greater peripheral speeds from the inlet toward the roller-type cutting means.

11. A roller-type cutter assembly for transporting, crushing. compacting, and cutting material in combination comprising:

A structural means for supporting said assembly;

a plurality of interposed roller-type cutting means rotatably mounted on the structural means, with each of said rollertype cutting means having spaced apart cutting edges disposed adjacent opposite end portions of said rollertype cutting means and each cutting edge so constructed and arranged to cooperate with a complementary cutting edge on an adjacent interposed roller-type cutting means to effectively cut material that is forced therebetween;

each roller-type cutting means having an outer cylinderlike surface with protuberance means disposed thereon for positively forcing the material into and through the cutting edges;

means for rotating the roller-type cutting means at a predetermined angular velocity;

at live-roll conveyor assembly including aligned roll members with each roll having an outer cylinderlike surface for transporting material being handled from a source of supply toward the roller-type cutting means, said live-roll conveyor assembly having an inlet positioned adjacent said source of supply and an outlet disposed adjacent said roller-type cutting means; and

means for rotatably mounting said roll members on the structural means.

. UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. v 3 y 643 a 591 I Dated Y Z2 1972 Charles Gail Bragg Inventor(s) It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:

In FIG. 1 of the drawing The arrow which indicate the direction of rotation of roller-type cutter 20, FIG. 1, erroneously indicates roller-type cutter 20 tobe rotating in a counterclockwise direction. The roller-type cutter 20 should rotate in a clockwise direction as defined in the specification.

Signed and sealed this 20th day of February 1973) (SEAL) Attest:

IZDWARI) ILFIE'ICIHZR,JR. ROBERT GOTTSCHALK /\CCStl11g Officer Commissioner of Patents FORM (10-69) USCOMM'DC 60376-P69 U45. GOVERNMENT PRINTNG OFFICE I I959 0"366'334, 

1. A roller-type cutter assembly for transporting, crushing, compacting, and cutting material in combination comprising: A structural means for supporting said assembly; a plurality of interposed roller-type cutting means rotatably mounted on the structural means, with each of said roller-type cutting means having spaced apart cutting edges disposed adjacent opposite end portions of said roller-type cutting means and each cutting edge so constructed and arranged to cooperate with a complementary cutting edge on an adjacent interposed roller-type cutting means to effectively cut material that is forced therebetween; each roller-type cutting means having an outer cylinderlike surface with protuberance means disposed thereon for positively forcing the material into and through the cutting edges; means for rotating the roller-type cutting means at a predetermined angular velocity; a live-roll conveyor assembly including aligned roll members with each roll having an outer cylinderlike surface for transporting material being handled from a source of supply toward the roller-type cutting means, said live-roll conveyor assembly having an inlet positioned adjacent said source of supply and an outlet disposed adjacent said roller-type cutting means; means for rotatably mounting said roll members on the structural means; and means for moving the cylinderlike outer surface of each roll member at a peripheral speed which is slower than the peripheral speed of the roller-type cutting means.
 2. The roller-type cutter assembly recited in claim 1, wherein each protuberance means is substantially coextensive with its respective roller-type cutting means.
 3. The roller-type cutter assembly recited in claim 2, wherein each protuberance means is a metal bar having a rectilinear configuration in cross section.
 4. The roller-type cutter assembly recited in claim 2, wherein each protuberance means has a rectilinear configuration in cross section.
 5. The roller-cutting assembly recited in claim 1, wherein the rotatable cutting means includes: A first series of roller-type cutters fixedly secured to a rotatable shaft, said cutters being spaced along the longitudinal length of said shaft, thereby forming an annular recess between each pair of adjacent roller-type cutters; a second series of roller-type cutters fixedly secured to another rotatable shaft, with said cutters spaced along the longitudinal length of the another shaft and thus forming an annular recess between each pair of adjacent roller-type cutters, with each roller-type cutter of the second series positioned opposite and a portion thereof extending into an opposite annular recess formed between adjacent roller-type cutters of said first series.
 6. The roller-type cutter assembly recited in claim 1, wherein the live-roll conveyor assembly includes a first live-roll conveyor disposed in opposed relationship with respect to a second live-roll conveyor, said first and second conveyors so constructed and arranged in a converging relationship from the inlet toward the outlet for simultaneously transporting, crushing, and compacting the material being handled as it moves from the source of supply toward the roller-type cutting means.
 7. The roller-type cutter assembly recited in claim 6, wherein the converging inclination of the first and second live-roll conveyors with respect to a horizontal plane is substantially the same.
 8. The roller-type cutter assembly recited in claim 7, wherein each protuberance means has an angular corner formed by a pair of intersecting planes, said corner so constructed and arranged for positively forcing the material handled into and through the cutting edges.
 9. The roller-type cutter assembly recited in claim 1, wherein the means for rotating the roller-type cutting means at a predetermined velocity includes torque transmitting means drivingly connected to the cutting means for effecting rotation thereof, said torque transmitting means including a belt drive assembly drivingly interconnecting a prime mover with a chain drive assembly that is drivingly connected at one end to a portion of said belt drive assembly and at another end to a gear drive means that is drivingly connected to the cutting means for rotating said cutting means at a predetermined angular velocity.
 10. The roller-type cutter assembly recited in claim 1, wherein the means for rotating the cylinderlike outer surface of each roll member includes means for moving the outer surface of adjacent roll members at progressively greater peripheral speeds from the inlet toward the roller-type cutting means.
 11. A roller-type cutter assembly for transporting, crushing, compacting, and cutting material in combination comprising: A structural means for supporting said assembly; a plurality of interposed roller-type cutting means rotatably mounted on the structural means, with each of said roller-type cutting means having spaced apart cutting edges disposed adjacent opposite end portions of said roller-type cutting means and each cutting edge so constructed and arranged to cooperate with a complementary cutting edge on an adjacent interposed roller-type cutting means to effectively cut material that is forced therebetween; each roller-type cutting means having an outer cylinderlike surface with protuberance means disposed thereon for positively forcing the material into and through the cutting edges; means for rotating the roller-type cutting means at a predetermined angular velocity; a live-roll conveyor assembly including aligned roll members with each roll having an outer cylinderlike surface for transporting material being handled from a source of supply toward the roller-type cutting means, said live-roll conveyor assembly having an inlet positioned adjacent said source of supply and an outlet disposed adjacent said roller-type cutting means; and means for rotatably mounting said roll members on the structural means. 